Dual ring burner ovni

ABSTRACT

There is disclosed a toroidal double ring flame burner comprising a toroidal cover with a lower wall and a burner body comprising a mixing tube which receives and emits a combustible-air pre-mixture; a mixing chamber which receives said pre-mixture and homogenizes it, creating a combustible-air mixture; a distribution channel for distributing the mixture; an inner crenellated wall and an outer crenellated wall, said crenellated walls are separated by the distribution channel and with at least main combustion ports and secondary combustion ports; over the inner crenellated wall, at least one inner barrier rail with combustion ports of inner barrier rail; over the outer crenellated wall, at least one outer barrier rail with combustion ports of outer barrier rail; over the outer crenellated wall at least one outer barrier rail with outer barrier rail combustion ports.

FIELD OF THE INVENTION

The present invention relates to a toroidal double ring burner which presents flames to the inner and to the outer parts of said ring, wherein the flames are inclined upwardly. The inclination of said flames of the ring increases the contact area of these with the receptacle, both towards the outer part as well as to the inner part of the ring, and thereby increases thermal efficacy of the burner.

BACKGROUND

A considerable amount of burners intended for use in household equipment exist in the marketplace, initially, the main objective for these was to make available a flame which would light up unto the utensils wishing to be heated, without considering aspects regarding the efficacy of use of the combustibles used for heating purposes or aspects of an ecologic character; with time the design of burners has had an evolution towards resolving the above mentioned aspects, among others.

BRIEF DESCRIPTION OF THE INVENTION

The present invention relates to a toroidal double ring flame burner comprising a toroidal cover lid with a lower wall and a burner body comprising a mixing tube which receives and emits a combustible-air pre-mixture; a mixing chamber which receives said pre-mixture and homogenizes it, creating an combustible-air mixture; a distribution channel for distributing the mixture; an inner crenellated wall and an outer crenellated wall, said crenellated walls are separated by the distribution channel and with at least main combustion ports and secondary combustion ports; over the inner crenellated wall, at least one inner barrier rail with combustion ports of inner barrier rail; over the outer crenellated wall, at least one outer barrier rail with combustion ports of outer barrier rail; a stability and flame transfer chamber with at least one wall which divides the distribution channel from the inner crenellated wall towards the outer crenellated wall, the at least one wall of the transfer chamber presents a central section and lateral sections, a first lateral section being in connection with at least one periphery crenel for stability and inner transfer and a second lateral section being in connection with at least one peripheral crenel for outer stability and transfer; in said at least one peripheral crenel for outer or inner stability and transfer, a radial combustion port for flame transfer is found.

BRIEF DESCRIPTION OF THE FIGURES

The illustrative embodiment may be described referencing the accompanying figures, which refer to:

FIG. 1 shows the mass flow of the combustible-air mixture in the burner of present invention in detail.

FIG. 2 shows a perspective view of the double ring toroidal burner.

FIG. 3 shows a perspective view of the body of the double ring toroidal burner.

FIG. 4 shows a longitudinal cut of the body of the double ring toroidal burner.

FIG. 5 shows a longitudinal cut of the body of the burner in detail.

FIG. 6 shows the combustion ports of the double ring toroidal burner in detail.

In FIGS. 6A and 6B the angle of inclination of the main inner peripheral combustion ports and of the secondary inner as well as outer peripheral combustion ports can be seen in detail.

In FIG. 7 the mixture chamber of the double ring toroidal burner can be seen in detail.

In FIGS. 7A and 7B the barrier rails of the double ring toroidal burner can be seen in detail.

In FIG. 8 the stability and transfer chamber of the double ring toroidal burner can be seen in detail.

In FIG. 8A the peripheral crenels for stability and transfer can be seen in detail.

In FIG. 8B the space formed between the peripheral crenels for stability and transfer, at least one wall of the chamber for stability and transfer and the toroidal cover lid can be seen in detail.

FIG. 9 shows a cross cut section view of the toroidal cover lid.

FIG. 10 shows a lower view of the double ring toroidal burner.

DETAILED DESCRIPTION OF THE INVENTION

The following description references FIGS. 1 through 10.

The use of the term “approximately” provides an additional determined range. The term is defined in the following manner. The additional range provided by the term is ±10%. By way of example, but not in a limitative manner, if it reads “approximately between 25° to 41°”, the exact range is between 22.5° and 45.1°, or yet between 27.5° and 45.1°, or yet between 22.5° and 36.9° or between 27.5° and 36.9°. Any of the possibilities described above are covered through the use of the term “approximately”.

In FIG. 1 a mass flow diagram of the burner of present invention is shown. A multiple selection valve is activated (not shown), in such a way that it allows the flow of combustible (3) from a nozzle and combustion port nozzle (7) towards a Venturi tube (104), in such a way that due to the difference in velocities, the primary air (1) is dragged towards the inner part of said Venturi tube (104), carrying out a combustible-air (4) pre-mixture which presents a turbulent flow, said combustible-air (4) pre-mixture which exits at a first velocity, is not sufficiently uniform to carry out an adequate dart flame ignition, so that the combustible-air (4) pre-mixture continues its trajectory along the length of the Venturi tube (104) and is expelled through the exit (223) of the Venturi tube (104), in such a way that upon flowing into the mixture chamber (237), said combustible-air (4) pre-mixture is homogenized in the surrounding areas of the exit of the venture tube (104), upon flowing from the same and knocking against the lower part of the toroidal cover lid (50) which forms part of the mixture chamber (237), where the final mixture of the combustible-air (9) takes place at a second velocity for decelerating or decreasing the energy of the mixture, and enters the barrier rails (225, 228), which help decrease the energy of the mixture for avoiding flame detachment in the combustion ports near the mixture chamber (237), afterwards it is distributed through the distribution channel (205) to be dosed in a controlled manner in the combustion ports and undertake an adequate dart flame ignition, additionally, said dart flame is fed by secondary air (2) emanating from the environment surroundings.

In FIG. 2 it is possible to see the double ring toroidal burner (100) of present invention, which comprises a body (20) of double rind toroidal burner, in such a way that the double ring toroidal burner (100) is found as a single piece, whether it is monolithic or integrated, in this case the term integrated refers to the body (20) of the double ring toroidal burner (100) and the Venturi tube (104) are manufactured separately and later joined, while the term monolithic refers to both the body (20) of the double ring toroidal burner (100) and the Venturi tube (104) which are manufactured through smelting into a single piece.

Over the body of the double ring toroidal burner (100) a toroidal cover lid (50) is provided.

In FIGS. 3 and 4 a perspective view of the body (20) of the double ring toroidal burner (100) can be seen, which comprises an upper surface (201) and a lower surface (202); on said upper surface (201) are found an inner crenellated wall (203) and an outer crenellated wall (204), which are preferably concentric, separated between them by a distribution channel (205); a mixture chamber (237) set above the exit (223) of the Venturi tube (104) between the inner (203) and outer (204) crenellated walls and delimited by the lower surface (501) of the toroidal cover lid (50), the first and second bevels (508, 511) of the toroidal cover lid (50) rest over the inner (203) and outer (204) crenellated walls sealing the distribution channel, the function of said mixture chamber (237) is to carry out the final mixing of the combustible-air pre-mixing (4) to form the combustible-air mixture (9) emanating from the Venturi tube (104).

In FIG. 5 a detail can be seen of the longitudinal cut of the body of the burner, where it can be seen that the outer crenellated wall (204) comprises three sections, a first section (207) which is substantially vertical and which extends from a back wall (206) of the distribution channel (205), a second section (208) which is inclined outwardly and upwardly from the highest part of the first vertical wall (207), the inclination angle (ε) of said second section is found within the range of approximately 25° and 45°, preferably approximately 35°, and a third section. (209) which is curved and extends outwardly and downwardly from the highest point of the second inclined section (208), said third curved section (209) extends up to a point under the inner surface of the back wall (206) of the distribution channel (205); the inner crenellated wall (203) comprises four sections, a first section (210) which is substantially vertical which extends from the back wall (206) of the distribution channel (205), a second section (211) inclined outwardly and upwardly from the highest part of the first substantially vertical section (210), the inclination angle (ζ) of said second section is found within the range of approximately 20° and 40°, preferably approximately 30°, a third curved section (212) which extends outwardly and downwardly from the highest point in the second section inclined up to a point which is slightly under the highest point of the first section (210) and a fourth vertical section (213) which extends downwardly from the lowest point of the third curved section (212) and up to a point underneath the highest point of the first section (210).

The back wall (206) of the distribution channel comprises three sections, a central section (214) and two outer sections (215, 216); the outer sections (215, 216) are inclined towards the central section (214) of said back wall (206), the end sections of the outer sections (215, 216) of said back wall (206) are higher than the central section (214) of said back wall (206); it should be noted that the distribution channel (205) has a transversal section which is uniform, in such a way that the area through which the flow of the combustible-air mixture (10) passes through is kept constant.

FIG. 6 shows details of the inner crenellated walls (203) and outer crenellated walls (204), said inner (203) and outer (204) crenellated walls present a first plurality of first radial grooves (217) at a first depth, while said inner (203) crenellated wall presents a second plurality of second radial grooves (2171) at a second depth, said second depth being greater than the first depth; said radial grooves form crenels (218) in said crenellated walls (203, 204), in such a way that said first and second radial grooves (217, 2171) from a plurality of main peripheral combustion ports, said combustion ports are divided into main primary inner peripheral combustion parts (2191), main secondary inner peripheral combustion ports (2193) and main outer peripheral combustion ports (2192), depending on the arrangement thereof, whether it be on the inner crenellated wall (203) or on the outer crenellated wall (204), said first and second grooves present a lower end and an upper end, the lower end being broader than the upper end, similarly, said lower end is rounded, the main peripheral combustion ports present a perimeter recess; the plurality of crenels (218) presents a third radial groove (220) at a third depth, the third depth being between 1/10 and ⅛ of the first depth, said third radial grooves (220) being wider than the first radial grooves on their upper end, the width of the first radial groove being between ¼ and ⅕ of the width of the third groove, said plurality of third radial grooves form a plurality of secondary peripheral combustion ports, which are divided into inner secondary peripheral combustion ports (2211) and outer secondary peripheral combustion ports (2212), depending on the arrangement thereof, whether it is on the inner crenellated wall (203) or on the outer crenellated wall (204).

In FIG. 6A the inclination angle (η) can be seen in regards to a horizontal plane of the main outer peripheral combustion ports (2192), which are found within a range between approximately 25° to 49°; preferably between approximately 30° to approximately 44°, preferably approximately 37°. Similarly, the inclination angle (θ) can be seen in regards to a horizontal plane of the primary inner peripheral combustion ports (2191) which is found within a range between approximately 20° to approximately 42°; preferably between approximately 25° to approximately 37°, preferably approximately 31°.

In FIG. 6B the inclination angle (τ) can be seen in regards to a horizontal plane of the secondary outer peripheral combustion ports (2212) as well as the inner ones (2211), which are found within a range between approximately 20° to 40°; preferably between approximately 27° to approximately 33°, preferably approximately 30°.

In an alternative embodiment, in FIGS. 3 and 4 it can be seen that on the third section (209) of the outer crenellated wall (204) an opening (400) is found where a spark plug (not shown) protrudes for the igniting of said toroidal double ring burner (100). Similarly, in another alternative embodiment, in the third (212) and fourth (213) sections of the inner crenellated wall (203) an opening is found (not shown) from which a spark plug (not shown) protrudes for the igniting of said toroidal double ring burner (100).

In FIG. 7 one can see in detail the mixture chamber (237) illustrated by way of lines and dots, where an exit (223) of the Venturi tube (104) is found, which is found set above the back wall (206) of the distribution channel (205); on the lower surface (202) of the body (20) of the toroidal double ring burner, in an alternative embodiment said Venturi tube and the body (20) of the toroidal double ring burner are found in a single monolithic body.

Attached to the exit of the Venturi tube (104) an inner barrier rail (225) is found on the inner wall (203) and an outer barrier rail (228) on the outer wall (204), said inner and outer barrier rails (225, 228) present a sinuous trajectory which follows the combustible-air mixture (10) prior to becoming fully incorporated into the distribution channel (205), so upon presenting a turbulent flow to the inner part of said barrier rails, the energy of the combustible-air (10) is dissipated and thus the particles which enter the combustion ports be able to have a lower velocity, thereby allowing adequate ignition of said final combustible-air mixture.

FIG. 7A shows said inner barrier rail (225) in detail, which comprises a first circumferential groove (226) concentric to the distribution channel (205) in the second section (208) of said inner crenellated wall (203) which is found in fluid communication solely with a pair of main inner peripheral combustion ports (2191) on the sides of said first groove (226), similarly, said first groove (226) presents a wall (2261) which avoids the direct ingress of the combustible-air mixture (10) into said inner barrier rail (225), said first circumferential groove (226), presents a plurality of radial grooves which come out of said inner segment (203), forming a plurality of inner barrier rail combustion ports (227) through which a part of the combustible-air mixture (10) is ignited once it has lost energy in said inner barrier rail, the depth of the first circumferential groove (226) is approximately ¼ and ⅕ the depth of the main inner peripheral combustion ports.

In FIG. 7B details can be seen of said outer barrier rail (228), which comprises a second circumferential groove (229) concentric to the distribution channel (205) thereby forming a wall (2291) which separates a second circumferential groove (229) from the distribution channel (205); along the length of said second circumferential groove (229) a radial groove is found at each end of said circumferential groove, as well as at least one radial groove between said end radial grooves, which come out of the outer crenellated wall (204), forming a plurality of combustion ports for an outer barrier rail (230); a plurality of communication grooves (231) which communicate a second circumferential groove (229) with the distribution channel (205), the plurality of combustion ports for an outer barrier rail (230) are found unaligned with the communication grooves (231); the depth of the second circumferential groove (229) is approximately between ½ and ⅔ the depth of the distribution channel (205).

FIG. 8 shows a detailed view of a stability and transfer flame chamber (232), which is found diametrically opposed to the exit (223) of the Venturi tube (104), said stability and transfer of flame chamber (232), transfers the flame from the inner crenellated wall (203) towards the outer crenellated wall (204) or vice versa, depending on where the ignition spark plug (not shown) is located; said stability and transfer of flame chamber (232) is found set between two main inner and outer peripheral combustion ports (219), in such a way that said main peripheral combustion ports (219) ignite the combustible-air mixture (10) which is found in said chamber (232); said stability and transfer of flame chamber (232) comprises and upper wall (238) and a pair of radial wails (233) which are parallel to each other and which are perpendicular to said upper wall (238), set between the inner (203) and outer (204) crenellated walls, substantially perpendicular to the back wall of the distribution channel (205); the upper wall is found in connection with a pair of peripheral crenels for stability and transfer (241) on the side, being inner and outer, said peripheral crenels for stability and transfer (241) present on their uppermost part a radial combustion port (243) for flame transfer, which transfers flame from the main peripheral combustion port (219) to the stability and transfer of flame chamber (232); between said peripheral crenels for stability and transfer (241) a combustion port for exiting the stability and transfer chamber (244) is found, which itself generates a dart flame both on the inner crenellated wall (203) as well as in the outer crenellated wall (204), said dart flame is what ignites the dart of the opposite end through the stability and transfer chamber (232).

In FIG. 8A it can be seen that the radial combustion port (243) for flame transfer presents an inclination angle (Ω) found within a range between approximately 60° to approximately 120°; preferably between approximately 80° to approximately 100°, preferably approximately 90°.

In FIG. 8B it can be seen in a detailed manner that the peripheral crenels for stability and transfer (241) present a height (h1) which is substantially lower than the height (h2) of the crenels (218) which form part of the inner and outer main peripheral combustion ports (219) in such a way that a free space is formed (242) between the toroidal cover lid (50) and said peripheral crenels for stability and transfer (241), through which the flame is transferred towards the inner part of the stability and transfer chamber (232).

Similarly, said toroidal double ring burner (100) presents a toroidal cover lid (50), preferably made of steel. Said toroidal cover lid (50) is placed over the peripheral combustion ports of the body (20) of the toroidal double ring burner (100).

In FIG. 9 it can be seen that said steel toroidal cover lid (50) presents a horizontal lower plane surface (501) which defines an upper limit for the distribution channel (205) and a curved upper surface (502), which presents an upper point (503) in close proximity to the outer end (504) of said cover lid, a first curvature (505) which extends from the upper point (503) towards the outer end (504) of the cover lid (50) and a second curvature (506) which extends from the upper point (503) towards the inner end (507) of the cover lid (50), the radius of the second curvature (506) being greater than that of the first curvature (505). The outer end (504) of the cover lid (50) extends above from the inner end (507); similarly the lower plane surface (501) joins with the inner end (507) of the cover lid (50) by means of a first rounded bevel (508) which presents an inclination angle (ζ′) which substantially coincides with the (ζ) inclination angle of the second section of the inner crenellated wall, the outer end (504) of the cover lid (50) presents a protuberance (509) with a substantially horizontal plane lower end (510), which itself joins with the lower plane surface (501) by means of a second bevel (511), said second bevel (511) presents an inclination angle (ε′) which is substantially coinciding with the inclination angle (ε) of the second section of inner crenellated wall. The main function of said protuberance (509) with the substantially horizontal plane lower end (510) is that of anchoring the flame dart to the burner.

FIG. 10 shows that on the lower surface (202) of the body (20) of the toroidal double ring burner (100) a plurality of concentric circumferential ribs (235) are found which serve as a reinforcement for the body (20) of the toroidal double ring burner (100), similarly, it presents a plurality of radial ribs (260), over each one of said radial ribs (260) a protrusion (236) is found in close proximity to the outer perimeter of said body (20) of the toroidal double ring burner, said protrusions (236) produce a separation between the plane of the cover (6) of burners which is the surface of the heating apparatus and the lower surface (20) of the body (20) of the burner, said separation allows the flow of secondary air (2) towards the combustion ports (2191, 2211) of the inner crenellated wall (203) of said body (20) of the toroidal double ring burner, as well as the main central combustion ports (117) of the central burner (10); the edge which the base of the burner forms with the inner crenellated wall (203), just underneath the combustion ports (219), has been provided a bevel or a radius, which allows for better air flow between the lower surface (202) of the toroidal burner (20) and the plane burner cover lid, taking more secondary air towards the combustion ports (2191, 2193, 220) of the inner crenellated wall (203). Said protrusions (236) may present any type of shape. The lower surface (202) of said body (20) of the toroidal double ring burner, additionally functions, as a cooling surface, given that upon the secondary air (2) circulating between said lower surface (202) and the cover prior to getting to the combustion ports, it cools the burner (100) of present invention, due to its irregular shape (see FIG. 1), the lower surface (202) offers a much greater area than if it was plane in order to undertake the correct cooling.

Said multiple flame burner (1) is placed over a support (not shown) which joins with a surface of the stove for example by means of perforations and screws, on this support, the Venturi tube (104) is housed, on the lower part of the support, a distributor for combustible is housed, unto which the corresponding nozzle and the combustion nozzle (7) are connected; the distributor of combustible is designed in such a way that it may be connected to a simple exit valve (not shown), thereby controlling the heating intensity.

The functioning of the toroidal double ring burner (100) of present invention is the following:

Said multiple selection valve (not shown) is activated, in such a way that it allows the flow of combustible from the nozzle and the combustion port nozzle (7) towards the Venturi tube (104), given the difference in velocities, primary air (1) from the surroundings is dragged towards the inner part of said Venturi tube (104), forming a combustible-air pre-mixture (4), which presents a turbulent flow which exits at a first velocity, which itself is not sufficiently uniform to carry out an adequate dart flame ignition, so that the combustible-air pre-mixture (4) continues its trajectory along the length of the Venturi tube (104) and is expelled through the exit (223) of the Venturi tube (104), said combustible-air pre-mixture (4) is homogenized in the proximal vicinity of the exit (223) of the Venturi tube (104), upon flowing out from the same and colliding against the lower part of the toroidal cover lid (50) which forms part of the mixture chamber (237), where the final combustible-air mixture (9) takes place at a second velocity in order to decelerate or decrease the energy of the mixture, and enters the barrier rails (225, 228), which help decrease the energy of the mix to avoid flame detachment in the combustion ports nearby to the mixture chamber (237), afterwards it is distributed through the distribution channel (205) to exit through the main inner peripheral combustion ports (2191) and the main outer peripheral combustion ports (2192), said mixture presents the sufficient uniformity to undertake an adequate dart flame ignition, the second velocity being lower than the first velocity, the combustible-air mixture which exits through the main inner peripheral combustion ports (2191) is ignited given the contact between the final combustible-air mixture with a spark emanating from a spark plug (not shown), once said flame dart is formed in the main inner peripheral combustion port (2191), this flame dart extends in a radial manner to the remaining main inner peripheral combustion ports (2191) means of secondary inner peripheral combustion ports (2211), afterwards a flame is transferred to the stability and transfer chamber (232), which then transfers the flame to the inner crenellated wall (203) towards the outer crenellated wall (204), igniting a flame dart on one of the main outer peripheral combustion ports (2192), this flame dart extends in a radial manner to the remaining main outer peripheral combustion ports (2192) by means of secondary outer peripheral combustion ports (2212), the mass of the combustible-air mixture which is burnt in the flame darts is the same as that which is formed in the mixture chamber (237), similarly, the exiting velocity of the combustible air mixture is determinant for the length of flame dart which is formed at the main inner and outer peripheral combustion ports, if the combustible-air mixture were to not decrease its velocity from a first velocity to a second velocity, the flame dart would completely detach from said double ring toroidal burner.

In an alternative embodiment, the spark plug (not shown) is found set in close proximity to the main outer peripheral combustion ports (2192), once said flame dart is formed at the main outer peripheral combustion ports (2192), this flame dart extends in a radial manner to the remaining main outer peripheral combustion ports (2192) by means of secondary outer peripheral combustion ports (2212), afterwards, a flame is transferred to the stability and transfer chamber (232), which then transfers the flame to the outer crenellated wall (204) towards the inner crenellated wall (203), igniting a flame dart on one of the main inner peripheral combustion ports (2191), this flame dart extends in a radial manner to the remaining main inner peripheral combustion ports (2191) by means of secondary inner peripheral combustion ports (2211).

In a second alternative embodiment there is no spark plug, so that the flame dart is ignited by means of the contact with an outer flame, which emanates from a lighter, a match etc.

Said double ring toroidal flame burner is found installed unto a household appliance, as could be a household stove, an industrial stove, a grill etc.

Alterations to the structure hereby described for the present invention can be foreseen by those persons skilled in the art. However, it should be understood that present description is related with the preferred embodiments of the invention, which is merely for illustrative purposes and should not be construed as a limitation of present invention. All obvious modifications in the scope of the invention, such as changes to the shape, material and sizes of the different elements which make up the invention, should be considered to lie within the scope of the attached claims. 

1. A double ring toroidal flame burner comprising: a toroidal cover lid with a lower wall and a burner body comprising: a mixture tube which receives and emits a combustible-air pre-mixture; a mixture chamber which receives said pre-mixture and homogenizes it, creating a combustible-air mixture; a distribution channel for distributing the mixture; an inner crenellated wall and an outer crenellated wall, said crenellated walls separated by the distribution channel and with at least main combustion ports and secondary combustion ports; over the inner crenellated wall, at least one inner barrier rail with inner barrier rail combustion ports; over the outer crenellated wall, at least one outer barrier rail with outer barrier rail combustion ports; and a stability and flame transfer chamber with at least one wall which divides the distribution channel from the inner crenellated wall until the outer crenellated wall, the at least one wall of the transfer chamber presents a central section and lateral sections, a first lateral section being in connection with at least one peripheral crenel for inner stability and transfer and a second lateral section being in connection with at least one peripheral crenel for outer stability and transfer; on said at least one peripheral crenel for stability and transfer, inner or outer, a radial combustion port for flame transfer is found.
 2. The burner according to claim 1, characterized by said inner and outer crenellated walls are concentric.
 3. The burner according to claim 1, wherein the outer crenellated wall comprises three sections, a first section substantially vertical which extends from a back wall of the distribution channel, a second section inclined outwardly and upwardly from the highest part of the first substantially vertical section and a third curved section which extends outwardly and downwardly from the highest point of the second inclined section, said third curved section extends up to a point under the inner surface of the back wall of the distribution channel, said third curved section presents at least one circumferential groove which feeds the flame with secondary air.
 4. The burner according to claim 1, wherein the inner crenellated wall comprises four sections, a first section substantially vertical which extends from the back wall of the distribution channel, a second section inclined outwardly and upwardly from the highest part of the first substantially vertical section, a third inclined section which extends outwardly and downwardly from the highest point on the second section inclined up to a point which is above the highest point of the first section and a fourth vertical section which extends downwardly from the lowest point of the third inclined section and up to a point above the highest point of the first section.
 5. The burner according to claim 3, wherein near the exit of the mixture tube the inner barrier rail is found, comprising a first circumferential groove concentric to the distribution channel in the second section of said inner crenellated wall which is found in fluid communication solely with a pair of main inner peripheral combustion ports on the sides of said first groove, said first circumferential groove presents a wall which avoids the direct ingress of the combustible-air mixture into said inner barrier rail, said first circumferential groove, presents a plurality of radial grooves which come out of the inner crenellated wall, forming a plurality of inner barrier rail combustion ports through which a part of the combustible air mixture is ignited once it has lost energy in said inner barrier rail, said outer barrier rail comprises a second circumferential groove with two ends, concentric to the distribution channel thereby forming a wall which separates the second circumferential groove from the distribution channel; along the length of said second circumferential groove a radial groove is found at each end of said circumferential groove, as well as at least one radial groove between said radial grooves, which come out of the outer crenellated wall, forming a plurality of combustion ports for an outer barrier rail; a plurality of communication grooves which communicate the second circumferential groove with the distribution channel, the plurality of combustion ports for an outer barrier rail are found unaligned with the communication grooves.
 6. The burner according to claim 1, wherein the lower surface of the body of the burner presents a plurality of concentric circumferential ribs and axial ribs which serve as a reinforcement for said body of the burner.
 7. The burner according to claim 6, characterized because set over at least two of the plurality of axial ribs a protrusion is found which produces a separation between the plane of the cover of burners and the lower surface of the body of the burner.
 8. The burner according to claim 1, wherein the lower wall of the toroidal cover lid defines an upper limit for the mixture chamber; the toroidal cover lid comprises a curved upper surface with an upper point in close proximity to the outer end of said cover lid, a first curvature which extends from the upper point towards the outer end, and a second curvature which extends from the upper point towards an inner end, the radius of the second curvature being greater than that of the first curvature; the outer end extends above the inner end of the cover lid; the lower surface is joined with the inner end by means of a rounded bevel, the outer end presents a protuberance with a substantially horizontal plane lower end, which itself joins with the lower surface by means of a bevel.
 9. The burner according to claim 1, wherein the inclination of the main peripheral combustion ports is found within a range between approximately 20° to approximately 49°.
 10. The burner according to claim 9, wherein the inclination of the main peripheral combustion ports is found within a range between approximately 25° to approximately 44°.
 11. The burner according to claim 10, wherein the inclination of the main peripheral combustion ports is found within a range between approximately 31° to approximately 37°.
 12. The burner according to claim 1, wherein the inclination of the secondary peripheral combustion ports is found within a range between approximately 20° to approximately 40°.
 13. The burner according to claim 12, wherein the inclination of the secondary peripheral combustion ports is found within a range between approximately 27° to approximately 33°.
 14. The burner according to claim 9, wherein the inclination of the secondary peripheral combustion ports is to be approximately 30°.
 15. The burner according to claim 1, wherein said radial combustion port for flame transfer presents an inclination angle within a range between approximately 60° to approximately 120°.
 16. The burner according to claim 15, wherein said radial combustion port for flame transfer presents an inclination angle within a range between approximately 80° to approximately 100°.
 17. The burner according to claim 16, wherein said radial combustion port for flame transfer presents an inclination angle of approximately 90°.
 18. The burner according to claim 1, wherein the height of the peripheral crenels for stability and transfer is substantially lesser than the height of the crenels which form the main inner and outer peripheral combustion ports, in such a way that a free space is formed between the toroidal cover lid and said peripheral crenels for stability and transfer.
 19. The burner according to claim 1, wherein between the combustion ports for stability and transfer of flame an exit port from the chamber of stability and transfer is found.
 20. A household appliance comprising a support surface and a double ring toroidal flame burner according to claim
 1. 